Hydraulic well pump



March 2, 1943. HUGHES 2,312,337

HYDRAULIC WELL PUMP Filed Jan. 29, 1940 3 Sheets-Sheet 1 March 2, 1943. HUGHES 2,312,337

HYDRAULIC WELL PUMP Filed Jan. 29, 1940 s Sheets-Shet 2 Frail Wm kg March 2,, 1943. L. E. HUGHES HYDRAULIC WELL PUMP Filed Jan. 29, 1940 3 Sheets-Sheet 3 Eatented Mar. 2, 1943 HYDRAULIC WELL PUMP Leigh 'E. Hughes, Indianapolis Ind. Application January 29, 1940, Serial No. 316,128

6 Claims.

This invention relates to improvements in deep well pumps and has for its object to provide a hydraulic pump having a plurality of completely separated hydraulic circuits.

Another object of the invention is to provide a hydraulically operated double stroke pump.

Another object of the invention is to provide, in a hydraulically operated pump, a power cylinder and an operating cylinder.

Another object of the invention is to provide in a deep well pump a double stroke pumping cylinder, an operating circuit and automatic means for restoring liquid to said circuit at such times as may be necessary.

A further object of the invention is to provide in a pump a hydraulic operating system embracing a power system and an operating system.

A still further object of the invention is to provide in a deep well pump means for preventing hammering or noise due to striking of the parts thereof with one another.

Another object of the invention is to provide a hydraulically operated pump including an operating fluid, under pressure, and means for controlling such pressure and automatically compensating for loss of any of said fluid.

A still further object of the invention is to make it possible to place the operating head at a distance from the well. I

A principal object of the invention is to provide in a hydraulically operated pump having a fluid actuated operating piston in which the load on one side of said piston is normally greater than on the other side, to provide means for carefully balancing the said fluid pressure with the load and to by-pass the fluid at the end of the stroke.

With the above and such other objects in view as may hereinafter more fully appear, I have invented the device shown in the accompanying drawings, in which: v

Figure 1 is' a diagrammatic elevational view illustrating my invention;

Figure 2 is a vertical sectional view of a pump head;

Figure 3 is a sectional view of a pressure control pump;

Figure 4 is a section on line 4-4 thereof;

Figure 5 is a bottom plan view thereof;

Figure 6 is a section on line 6-6 of Figure 2; enlarged;

Figure '7 is a diagrammatic view of a pressure control system;

Figure 8 is a longitudinal section of a pumping mechanism;

Figure 9 is a diagrammatic view, showing the connection between the cylinder of Figure 8, with the oil pump of Figure 2;

Figure 10 is an enlarged section on line Ill-l0 of Figure 8;

Figure 11 is a similar view taken on line I 1- of Figure 8;

Figure 12 is a similar of Figure 8;

Figure 13 is an enlarged section on line i3i3 of Figure 8;

Figure 14 is a similar view on line I i-M of Figure 8; and

Figure 15 is a section on line l5-l 5 of Figure 13.

Figure 16 is an enlarged diagrammatic sectional detail of a motor cylinder;

Figure 1'7 is a vertical section on line l'l-ll of Figure 3;

Figure 18 is a vertical section Figure 19;

Figure 19 is a horizontal section on line i9| 9 of Figure 8.

Like reference characters indicate like parts throughout the following several views in the drawings in which I indicates a hydraulic deep well pump constructed in accordance with my invention, and which pump embraces a pump head 2, upon which is mounted, or otherwise connected, a motor 3 for operating the crank 4 through the gear 5, see Figs. 1, 2 and 9, or other connection. Mounted on the housing 6 of the pump head is a pressure control and fluid review taken on line 12-.2

on line l8l8 of placement pump 1, see Figs. 2, 3, 7 and 17, having cylinders 8 and 9, see Figs. 3 and 17 connected at their lower ends by reduced bores l0 and H to bores I2 and I3. Normally closing the lower ends of ports 10 and H are ball valves i4 and i5, pressed by springs l6 and lower ends of ports or bores 12 and 13 are tubes i8 and 19. The lower end of tube 18 is threaded into the three-way connection 20, see lower end of Fig. 2 and the lower end of tube I9 is threaded to the three-way connection 2| thereabove. There is another bore 22 in the cylinder block 23, see Figs. 3, 4, and 1'7, to which is threaded the tube 24, the other end 25 of which is connected to the port 26 of a bore 21 passing down through block 28, see Fig. 2, extending from the intermediate portion of the housing 6. The passage 21 extends vertically down to and enters the transverse passage 29 in said block 28, said latter passage conmeeting at its outer end with a bore 30 in said block 28, and being connected through the port 3 l, controlled by the ball valve 32, to the relatively large bore 33 to which the three-way connection 21 is threaded at one inlet. The ball 32 is pressed specification and in the I1. Threaded into the by a spring 34, th tension of which is controlled by a'screw plug 35. The inner end of passage 29 opens into the oil sump 36 provided in the upper chamber 31 of housing 6, while the inner end of passage 33 enters the upper end 6| of a cylinder 38 in the pedestal 39 of said pump head 2, see Fig. 2, said cylinder being separated from cham .ber 31 by the wall 40. The bore 22 enters a cross bore 4| (see Figs. 3 and 4), one end being connected with cylinder 8, and the other end with cylinder 9 of said pump 1, and both ends of said bore 4| are controlled by spring pressed ball valves 42 and 43 (see Fig. '7 and Fig. 4) A bore 44 connects member 20 with a passage 45, see Fig. '7, in block 28 with the sump 36' said passage being controlled by a spring pressed ball valve 46, see Fig. 7, the tension of which is adjustable through screw plug 41.

The end 48 of crank 4 extends beyond its hearing 49 (see Fig. 2), to operate the pistons 50 and 6|, see Figs. 2, 3 and 17, through its cams 50' and which pistons are provided with heads 52 and 53, between which and the head of block 23 are provided springs 54 and 55 for raising of the pistons. Operating on the crank 4 is the connecting rod 56, see Fig. 2, connected to a piston rod 51 by a cross head 58. The rod 51 operates through a packing box 59 in the wall 40, and carries the piston 60 operating in the cylinder 38, said piston separating the cylinder into two chambers -BI above the piston and 62 below the piston. As above indicated, the passage 33 enters at the top of the chamber 6| and the passage 63 at the bottom ofthe chamber 62 has one port of the three-way connection threaded thereto.

As shown in Figs. 2 to 7, inclusive, the piston 60 in cylinder 8 draws liquid from reservoir 36 through 29, 21, 25, 24 et cetera and discharges same under pressure by line 8 to end 62 of cylinder 38, excess flowing through bore 44 and escaping through adjustable pressure relief valve 40 to chamber 45 in free communication with reservoir 36 by line 29, see Fig. 7. This is a closed cycle for make-up liquid supply.

In like manner, piston 5| in cylinder 9 draws liquid from reservoir 36 through 29, 21, 25, 24, et cetera, and discharge same under pressure by line l9 to end 6| of cylinder 38, excess flowing through bore 3| and escaping through adjustable pressure relief valve 32 to chamber 34 in free communication with reservoir 36 as at 29, see Figs.6and 7.

This is a second closed cycle for make-up liquid supply and these two liquid circuits normally are independent of each other except for the conmion reservoir 38, the common suction line 24 and the common discharge line 29, see Fig.

6, for in this diagrammatic view the line 29' extends oppositely from the lower end of chamber 36 positioned between chambers 34 and 35 and at the outer ends is. connected thereto, so the three chambers,34, 45 and 36 are in free communication. The only communication between these systems is that shown at the make-up supply end and in Figs. 9 and 16 that shown at the power piston cylinder end in Fig. 16, and otherwise reierred to herein.

Threaded to one port of said member 20 is pipe line '64 and threaded to one port of the connection 2| is a pipe line 65, both of which lines, see Figs. 9 and 16, extend down into a well and terminate in ports 66 and 61 in a cylinder 68. It is through the action of the fluid in the cylinder 68 that the water pumping piston 69 in cylinder which will be referred to numerically a little later on; however, it is, of course obvious that some of these elements may be independent of the said piping lI, if found desirable for any par icuiar purpose. Operating in the cylinder 68 is the upper end 12 of a piston rod 13 said upper end carrying a piston I4 which separates said cylinder into chambers 15 above the piston, and I6 below the piston. The lower end 11 of the pipe line 64 enters chamber 15 through port 66, (see Figs. 15, 16 and 18), and the lower end I8 of pipe line 65 enters the bottom of chamber I6 through port 61. A by-pass 19 leads from the upper end of chamber 15 to pipe line 64 and is controlled by a spring pressed ball valve 80. Said by-pas is so located that it will come just below the bottom wall of piston 14, when in its uppermost position. Another by-pass 8| is provided in the lower part of said chamber I5 just above the upper wall of said piston 14, when in its lowermost position. This by-pass leads to the pipe 65 and is controlled by a spring pressed ball valve 82.

A buffer spring 83 is fixed to the upper wall 84 of cylinder 68 and a similar spring 85 is attached to the bottom wall 86 of said cylinder in order to obviate any possibility of hammering of the piston in this cylinder. On the lower end 81 of the piston rod 13 is carried the piston '99 (see Fig. 8), operating in said water pumpingcylinder I0, which has a reduced portion 88. on one side of wall 89 of which is seated a valv 00 normally covering passage 90' and on the opposite wall 9 I of which is a screw plug 92 through which said valve may be seated. In the lower end of the pipe line H, just below the cylinder "I0, is a valve case 93, carrying the removable core 98 which separates said case into the water inlet port 95 and chambers 96 and 91, and passage 98 by means oI-its sinuously arranged center wall 99 and the valves I00, IN and I02. The said formation of wall 99 permits of the use of much larger valves than otherwise could be used within the comparative diameter of the casing 93.

Crank 4, see Fig. 9, operates piston 60 to drive oil down through pipe 64 to port 66 in cylinder 98 (chamber I6 being at this time filled with oil). Piston I4 in said cylinder being driven down moves piston 69 in cylinder 10 which action drives water in chamber 91 through valve I82 into passage 98in turn driving the water therein up through water pipe line 1| to tank I. The reverse action of the oil piston 60 drives the oil from chamber 6| 0! cylinder 38 through pipe 95 into lower chamber 16 oil cylinder 68, driving piston I4 up forcing the oil in chamber I5 back up through pipe 64 in to cylinder 38. This action, of course, raises piston 69 in cylinder I0 drawing water in through port 95 and through valves I0| into chamber 91 and cylinder I0.

The down movement of piston 69 drives water in chamber 91 through valve I02 into chamber 96 forcing water therein through passage 98 out through connections I03 into pipe line H. Chamber 96 connects with the upper end I04 of cylinder 10, through port I05 and exhausts into passage 98 through valve 90 as the piston 99 rises.

Chamber 96 is filled from passage 95 through valve I00 when piston 69 ismoved downwardly. The water piston 69 is double acting for supan elongated discharge chamber in the upper plying water under pressure to line H for each direction of movement of piston 89. Also piston 69 is power operable by piston 14 in each direction and by oil pressure from the piston 60 in each direction of its movement.

Pumps of this general character heretofore tried out have failed to properly function due to the fact that no practical automatic means has heretofore been provided for maintaining the exact necessary fluid pressure in the oil system for operating piston 14 which operates piston 69, therefore as leakage or evaporation or other exhaustion is bound to occur in the system, the failure of the proper action of the pump results. I have overcome this difiiculty, in my pump, through the automatic means for resupplying oil, or other operating fluid, as needed and in maintaining the same at proper pressure through the following means: An extra supply of the operating fluid is provided in the oil sump 85 immediately above cylinder 38, see Fig. 2, through the port 29 of which the fluid may pass, either through ports ill, entering outlet 33, the bored passage d'i into passage 2B, or the passage El into pipe 2t, oil pump inlet 22, thence to the passage M from whence it may be drawn through valves 42 and 83 into cylinders B and 9, on the up stroke of pistons 50 and 5| operated by the cams. On the down stroke of said pistons the oil in cylinders 8 and 9 is forced down through the valve controlled ports i and ii, through pipe lines I8 and i9, connections 20 and-2|, pipe lines t l and 65 and into the upper and lower chambers I and 76 of cylinder 68 through the ports 68 and Bl, consecutively, thus aiding in driving piston 14, first up and then down, which, in turn operates water piston 69 through their common piston rod 13. The by-passes 19 and BI controlled by valves 80 and 82, are provided to prevent the piston I4 from creeping at either end of the cylinder lit, and causing a hammer in the pumping operation. Springs 83 and 85 are used to further obviate striking of the piston against the cylinder ends. -It is clearly obvious that through the above explained system the exact necessary fluid pressure for perfect operation is at all times maintained, and that the necessary quantity of fluid in the system is also automatically maintained at all times, no matter what the cause of loss therefrom, other than failure to keep a sufllclent supply of oil in the sump 38.

Having now described my invention, that which I claim to be new, and desire to procure by Letters Patent is:

l. A compact, well bore receivable and submersible combination pressure liquid operable motor and liquid pump of double acting character including an upper cylinder, a power piston therein alternately subject to pressure liquid and at opposite ends for piston reciprocation, a second cylinder therebeneath and in longitudinal alignment therewith, a piston therein, a single rod rigidly connecting the adjacent ends of said pistons for second piston reciprocation with and by the first piston for pumping purposes. and a pair of pressure fluid supplying conduits each connected at its lower end to an end of the first mentioned cylinder for alternately supplying pressure thereto. a pump discharge pipe between the supply conduits and having-nested relation therewith, an elongated, unitary pump structure suspended therefrom and in operative communication with the discharge pipe and'mechanically including the second mentioned cylinder,

end of the unitary pump structure and communicating with the discharge pipe and offset laterally of the second mentioned cylinder, opposite ends of the latter discharging to the chamber, a check valve for each pump cylinder discharge, an intake chamber beneath the pump cylinder and also communicating with each end thereof. and a check valve for each intake communication, the several valves being superposed relative to each other, and each having its axis non-parallel to the rod axis, the check valves of the lower cylinder end being positioned between the check valves of the upper cylinder end, the intake check valve of each being below the dis charge check valve, the check controlled intake to the upper cylinder end lying parallel to the check controlled discharge from the lower cylinder end for an appreciable portion of their respective lengths. 2. A compact, well bore receivable and submersible combination pressure liquid operable motor and liquid pump of double acting character including an upper cylinder, 2. power piston therein alternately subject to pressure liquid and at opposite ends for piston reciprocation, a second cylinder therebeneath and in longitudinal alignment therewith, a piston therein, a single rod rigidly connecting the adjacent ends of said pistons for second piston reciprocation with and by the first piston for pumping pur poses, and a pair of pressure fluid supplying conduits each connected at its lower end for alter nately supplying pressure thereto to an end of the first mentioned cylinder, a pump discharge pipe between the supply conduits and having nested relation therewith, an elongatedunitary pump structure suspended therefrom and in operative communication with the discharge pipe and mechanically including the second mentioned cylinder, an elongated discharge chamber in the'upper end of the unitary pump structure nd communicating with the discharge pipe and offset laterally of the second mentioned cylinder,

opposite ends of the latter discharging to onposite ends of the chamber, a check valve for each pump cylinder discharge, an intake chamber beneath the pump cylinder, independent side by side intakes communicating with the chamber at their lower ends and at the upper end with the cylinder, and a check valve in each intake communication, to the intake chamber, the valves being superposed relative to each other, each valve having its axis extending angularly of the elongated pump structure axis permitting use of maximum size valves in the minimum cross-sectional area of said'structure substantially as described and illustrated.

3. In a pumping system including a pump piston and cylinder unit for pressure pumping, a second and power piston and cylinder unit, the pistons thereof being directly connected together,

vconstant pressure fluid supply means; and means independently connecting opposite ends of the second cylinder thereto for communication therewith, of a check controlled bypass for each means and at the end thereof immediately ad- Jacent the second cylinder and preventing pressure liquid flow from said means to the second cylinder but permitting liquid flow from second mentioned cylinder to that means under predetermined cylinder pressure, said bypasses, where connected with the second cylinder near the ends thereof, being spaced from the respective means connection thereto and more remote from the adjacent cylinder end than the adjacent means connection, the spacing between each bypass and between the adjacent means connection to the cylinder being at least as great as the length of the piston in said cylinder, the piston in that cylinder at each end of the piston stroke simultaneously exposing both bypass cylinder connections to the cylinder and on the same side of the piston therein.

4. A pumping system as defined by claim 3, characterized by said second cylinder at each end thereof including piston cushioning means.

5. A pumping system as defined by claim 3, characterized by said bypasses with saidsecond cylinder constituting the sole communication between said independent means, said sole communication only occurring when the second cylinder piston is at either end of said second cylinder and both bypasses are exposed to said second cylinder on the same side of the piston therein.

6. In a pressure liquid operable motor and liquid pump of double acting character including a cylinder, a power piston therein alternately subject to pressure liquid and at opposite ends for piston reciprocation, a second cylinder therebeneath and in longitudinal alignment therewith, a piston therein, rod means rigidly connecting the adjacent ends of said pistons for second piston reciprocation with and by the first piston for pumping purposes, and a pair of pressure fluid supplying conduits each connected to an end of the first mentioned cylinder, the combination of a discharge pipe, an elongated unitary structure suspended therefrom and in operative communication with the discharge pipe and mechanically including the second mentioned cylinder, an elongated discharge chamber in the upper end of the structure communicating with the discharge pipe and offset laterally of the second mentioned cylinder, opposite ends of the latter discharging to the chamber, a check valve for each discharge, an intake chamber beneath and communicating with each end of the second mentioned cylinder, and a check valve for each intake communication, the valves being superposed relative to each other, each valve having its axis extending angularly of the longi tudinal axis of the structure permitting use of maximum size valves in a minimum cross-sectional area of the arrangement substantially as described and illustrated.

LEIGH E. HUGHES. 

